WO2018221077A1

WO2018221077A1 - Electromagnetic valve, electromagnetic inlet valve mechanism, and high-pressure fuel pump

Info

Publication number: WO2018221077A1
Application number: PCT/JP2018/016525
Authority: WO
Inventors: 斉藤　淳治; 悟史臼井; 雅史根本; 壮嗣秋山; 千彰徳丸; 康久内山; 早谷　政彦; 小野瀬　亨; 亘枇本; 登住谷
Original assignee: 日立オートモティブシステムズ株式会社
Priority date: 2017-05-31
Filing date: 2018-04-24
Publication date: 2018-12-06
Also published as: CN110651117B; JP6840238B2; JPWO2018221077A1; CN110651117A; DE112018002027T5

Abstract

Provided are an electromagnetic valve, an electromagnetic inlet valve mechanism, and a high-pressure fuel pump that suppress movement of an inlet valve in the radial direction and improve flow rate controllability even when pressure becomes high or flow rate becomes high. This valve mechanism is provided with: a spring member that includes an end coil section and a movable section and that is secured by a spring support section on the side opposite the end coil section; and a valve body that is biased by the end coil section-side of the spring member. The valve body has formed therein a protrusion section that protrudes toward the spring support section-side and that is located on the radially inner side of the spring member. In a cross-section that passes through the radial center of the spring member and is cut in the spring member axial direction, a tip section of the protrusion section is positioned on the spring support section-side with respect to a coil cross-section on both sides of at least the first turn of the movable section that is adjacent to the end coil section.

Description

Electromagnetic valve, electromagnetic intake valve mechanism, and high-pressure fuel pump

The present invention relates to an electromagnetic valve, an electromagnetic intake valve mechanism, and a high-pressure fuel pump.

The background art of the high-pressure fuel pump of the present invention includes those described in Patent Documents 1 and 2. Patent Document 1 discloses that “a pump housing 1, a plunger 2, and an electromagnetic intake valve 300 are provided. The electromagnetic intake valve 300 includes a valve 301c and a valve seat 302a that opens and closes a fuel passage when the valve 301c is separated. And a valve stopper 313 against which the valve 301c abuts when the valve is opened. The electromagnetic intake valve 300 is attached to the electromagnetic intake valve insertion hole 1k formed in the pump housing 1, and the amount of discharged fuel is controlled by controlling the electromagnetic intake valve 300. In the high-pressure fuel pump to be controlled, the electromagnetic suction valve insertion hole 1k is provided with a bottom 1ka that contacts the valve stopper 313 and a fuel passage hole 1a that passes through the bottom 1ka and communicates with both sides of the bottom 1ka. (See summary).

Further, Patent Document 2 states that “the housing body 11 having the fuel passage 100 that guides fuel to the pressurizing chamber 121, the valve body 30 provided in the fuel passage 100, and the valve seat 34 of the valve body 30 are seated on or separated from the valve seat. A valve member 40 comprising a disc portion 41 to be seated and a hollow cylindrical guide portion 42, a stopper 50 having a cylindrical portion 51, a needle 60 that can contact the valve member 40, and a needle 60 that is connected to the valve member 40. And an electromagnetic drive unit 70 that can be attracted in the valve closing direction, and the stopper 50 covers the side wall surface of the pressure chamber 121 of the valve member 40 so as to hide when viewed from the pressure chamber 121 side. The guide portion 42 has, on the inner wall, a cylindrical guide surface 43 that can slide on the outer wall of the cylindrical portion 51 of the stopper 50. The spring 21 has at least a portion of the shaft surface of the guide surface 43 in the axial direction. At least part of the direction It is provided so as to overlap. "To be disclosed (see Abstract).

Japanese Unexamined Patent Publication No. 2016-191367 JP 2010-156264 A

However, in the case of the intake valve structure described in Patent Document 1, this movement cannot be restricted when the intake valve is tilted by a force in the radial direction or is shaken in the radial direction. If it does so, the sheet | seat by an intake valve will not be produced, but there exists a problem of causing the flow volume fall or the deterioration of flow controllability. Further, when the intake valve is inclined and comes into contact with the intake valve seat portion, the intake valve seat portion is worn, thereby causing a problem that the seat performance is deteriorated.

On the other hand, in the case of the suction valve described in Patent Document 2, the convex portion of the suction valve is slidably guided by the inner diameter cylinder of the valve holder. However, in this structure, it is necessary to process a recess for holding the spring on the convex portion of the intake valve, and a high processing accuracy is required, and a part for holding the spring (the recess) ) Would increase the cost.

Therefore, the present invention provides an electromagnetic valve, an electromagnetic intake valve mechanism, or a high-pressure fuel pump that suppresses radial movement of the intake valve and improves flow controllability even when the pressure is increased and the flow rate is increased. The purpose is to do.

In order to solve the above problems, a valve mechanism according to the present invention includes a spring winding portion and a movable portion, and is fixed by a spring support portion on a side opposite to the winding end portion, and the seat of the spring member. A valve body that is biased by the winding portion side, and a convex portion that is convex toward the spring support portion and that is positioned radially inside the spring member is formed on the valve body, and the spring In a cross-sectional view passing through the radial center of the member and cut in the axial direction of the spring member, the tip of the convex portion with respect to at least the first winding radial cross section of the movable portion adjacent to the end turn portion The part is configured to be located on the spring support side.

According to the present invention, an electromagnetic valve, an electromagnetic intake valve mechanism, or a high-pressure fuel pump that suppresses the radial movement of the intake valve and improves the flow rate controllability even when the pressure is increased and the flow rate is increased. It becomes possible to provide.
Problems, configurations, and effects other than those described above will be clarified by the following description of embodiments.

It is whole sectional drawing cut | disconnected and shown to the axial direction of a plunger about a high pressure fuel pump. FIG. 3 is an overall cross-sectional view showing the high-pressure fuel pump cut in a direction perpendicular to the axial direction of the plunger, and is a cross-sectional view at the fuel inlet shaft center and discharge port shaft center. FIG. 2 is an overall cross-sectional view of the high-pressure fuel pump at an angle different from that of FIG. It is the figure which expanded the longitudinal cross-sectional view of the electromagnetic suction valve mechanism of a high pressure fuel pump. It is a figure showing the whole system composition including a high-pressure fuel pump. It is a figure which expands and demonstrates the intake valve structure of the high pressure fuel pump of the Example of this invention. It is a figure which expands and demonstrates the suction valve structure of the state in which the valve body (suction valve 30) of the Example of this invention was seated on the valve seat (suction valve seat part 31a). It is a figure which expands and demonstrates the suction valve structure of the state in which the valve body (suction valve 30) of the Example of this invention contacted the stopper 32. FIG.

Hereinafter, the configuration and operational effects of the high-pressure fuel pump according to the embodiment of the present invention will be described with reference to the drawings. The high-pressure fuel pump of the present embodiment is a high-pressure fuel pump that discharges high-pressure fuel of 20 MPa or more. In each figure, the same numerals indicate the same parts.

(overall structure)
First, the configuration and operation of the system will be described using the overall configuration diagram of the engine system shown in FIG. A portion surrounded by a broken line indicates a main body of the high-pressure fuel pump, and a mechanism / part shown in the broken line is integrated in the pump body 1.

Fuel in the fuel tank 20 is pumped up by a feed pump 21 based on a signal from an engine control unit 27 (hereinafter referred to as ECU). This fuel is pressurized to an appropriate feed pressure and sent to the low pressure fuel inlet 10a of the high pressure fuel pump through the suction pipe 28. The fuel that has passed through the suction joint 51 (see FIG. 2) from the low-pressure fuel suction port 10a passes through the metal damper 9 (pressure pulsation reducing mechanism) and the suction passage 10d, and the suction port 31b of the electromagnetic suction valve mechanism 300 constituting the variable capacity mechanism. To.

The fuel that has flowed into the electromagnetic suction valve mechanism 300 passes through the suction valve 30 and flows into the pressurizing chamber 11.
The reciprocating power is applied to the plunger 2 by the cam 93 (see FIG. 1) of the engine (internal combustion engine). The reciprocating motion of the plunger 2 sucks fuel from the suction valve 30 during the downward stroke of the plunger 2 and pressurizes the fuel during the upward stroke. Through the discharge valve mechanism 8, the fuel is pumped to the common rail 23 to which the pressure sensor 26 is attached. The injector 24 injects fuel into the engine based on a signal from the ECU 27. This embodiment is a high pressure fuel pump applied to a so-called direct injection engine system in which an injector 24 directly injects fuel into a cylinder cylinder of an engine. The high-pressure fuel pump discharges the desired fuel flow rate of the supplied fuel in response to a signal from the ECU 27 to the electromagnetic intake valve mechanism 300.

(Configuration of high-pressure fuel pump)
Next, the configuration of the high-pressure fuel pump will be described with reference to FIGS. FIG. 1 is a longitudinal sectional view of a high-pressure fuel pump, and FIG. 2 is a horizontal sectional view of the high-pressure fuel pump as viewed from above. FIG. 3 is a longitudinal sectional view of the high-pressure fuel pump as seen from a different direction from FIG. FIG. 4 is an enlarged view of the electromagnetic suction valve mechanism 300.

As shown in FIG. 1, the high-pressure fuel pump is attached to the metal damper 9, the pump body 1 (pump main body) in which the damper accommodating portion 1 p for accommodating the metal damper 9 is formed, and the pump body 1. A damper cover 14 that covers 1p and holds the metal damper 9 between the pump body 1 and a holding member 9a that is fixed to the damper cover 14 and holds the metal damper 9 from the opposite side of the damper cover 14. Yes. The holding member 9 a is disposed between the metal damper 9 and the pump body 1, and holds the metal damper 9 from the pump body 1 side. The high-pressure fuel pump is attached to a high-pressure fuel pump mounting portion 90 of the internal combustion engine using a mounting flange 1e (see FIG. 2) provided in the pump body 1, and is fixed with a plurality of bolts.

As shown in FIG. 1, an O-ring 61 is fitted into the pump body 1 for sealing between the high-pressure fuel pump mounting portion 90 and the pump body 1 to prevent the engine oil from leaking to the outside. A cylinder 6 that guides the reciprocating motion of the plunger 2 and forms a pressurizing chamber 11 together with the pump body 1 is attached to the pump body 1. An electromagnetic suction valve mechanism 300 for supplying fuel to the pressurizing chamber 11 and a discharge valve mechanism 8 (see FIG. 2) for discharging fuel from the pressurizing chamber 11 to the discharge passage are provided.

As shown in FIG. 1, the cylinder 6 is press-fitted with the pump body 1 on the outer peripheral side thereof, and further, in the fixing portion 6 a, the body is deformed to the inner peripheral side to press the cylinder 6 upward in the figure. The fuel pressurized in the pressurizing chamber 11 is sealed so as not to leak to the low pressure side. At the lower end of the plunger 2 is provided a tappet 92 that converts the rotational movement of a cam 93 (cam mechanism) attached to the camshaft of the internal combustion engine into a vertical movement and transmits it to the plunger 2. The plunger 2 is pressure-bonded to the tappet 92 by the spring 4 through the retainer 15. Thereby, the plunger 2 can be reciprocated up and down with the rotational movement of the cam 93.

Also, the plunger seal 13 held at the lower end of the inner periphery of the seal holder 7 is installed in a slidable contact with the outer periphery of the plunger 2 at the lower part of the cylinder 6 in the figure. Thereby, when the plunger 2 slides, the fuel in the sub chamber 7a is sealed and prevented from flowing into the internal combustion engine. At the same time, lubricating oil (including engine oil) for lubricating the sliding portion in the internal combustion engine is prevented from flowing into the pump body 1.

A suction joint 51 is attached to the side surface of the pump body 1 of the high-pressure fuel pump. The suction joint 51 is connected to a low-pressure pipe that supplies fuel from the fuel tank 20 of the vehicle, and the fuel is supplied from here to the inside of the high-pressure fuel pump. The suction filter 52 (see FIG. 3) in the suction joint 51 serves to prevent foreign matters existing between the fuel tank 20 and the low-pressure fuel inlet 10a from being absorbed into the high-pressure fuel pump by the flow of fuel.
As shown in FIG. 1, the fuel that has passed through the low-pressure fuel intake port 10a reaches the intake port 31b of the electromagnetic intake valve mechanism 300 through the metal damper 9 and the intake passage 10d (low-pressure fuel flow path).

The electromagnetic suction valve mechanism 300 will be described in detail with reference to FIG. 1, 2, and 4 show the electromagnetic suction / inlet valve mechanism 300, but the structure shown in these drawings shows the case where the present invention is not applied.

The coil section includes a first yoke 42, an electromagnetic coil 43, a second yoke 44, a bobbin 45, a terminal 46, and a connector 47. A coil 43 in which a copper wire is wound around the bobbin 45 is disposed so as to be surrounded by the first yoke 42 and the second yoke 44, and is molded and fixed integrally with a connector which is a resin member. The respective ends of the two terminals 46 are respectively connected to both ends of the copper wire of the coil so as to be energized. Similarly, the terminal 46 is molded integrally with the connector, and the remaining end can be connected to the engine control unit side.

The coil portion is fixed by press-fitting the central hole of the first yoke 42 into the outer core 38. At that time, the inner diameter side of the second yoke 44 is in contact with the fixed core 39 or close to a slight clearance.

Both the first yoke 42 and the second yoke 44 are made of magnetic stainless steel in order to constitute a magnetic circuit and in consideration of corrosion resistance, and the bobbin 45 and the connector 47 are made of high strength heat resistant resin in consideration of strength characteristics and heat resistance characteristics. . The coil 43 is made of copper, and the terminal 46 is made of brass plated with metal.

Thus, when a magnetic circuit is formed by the outer core 38, the first yoke 42, the second yoke 44, the fixed core 39, and the anchor portion 36, and a current is applied to the coil, magnetic attraction is performed between the fixed core 39 and the anchor portion 36. A force is generated, and a force that is attracted to each other is generated. In the outer core 38, the axial portion where the fixed core 39 and the anchor portion 36 generate the magnetic attractive force is made as thin as possible, so that almost all of the magnetic flux passes between the fixed core 39 and the anchor portion 36. The magnetic attractive force can be obtained efficiently.

The solenoid mechanism part includes a rod 35 that is a movable part, an anchor part 36, a rod guide 37 that is a fixed part, an outer core 38, a fixed core 39, a rod biasing spring 40, and an anchor part biasing spring 41.

The rod 35 and the anchor part 36 which are movable parts are configured as separate members. The rod 35 is slidably held in the axial direction on the inner peripheral side of the rod guide 37, and the inner peripheral side of the anchor portion 36 is slidably held on the outer peripheral side of the rod 35. That is, both the rod 35 and the anchor portion 36 are configured to be slidable in the axial direction as long as they are geometrically restricted.

The anchor portion 36 has one or more through holes 36a penetrating in the axial direction of the component in order to move freely and smoothly in the axial direction in the fuel, and eliminates the restriction of movement due to the pressure difference before and after the anchor portion as much as possible. .

The rod guide 37 is inserted in the radial direction on the inner peripheral side of the hole into which the suction valve of the pump body 1 is inserted, and is abutted against one end of the suction valve seat in the axial direction and welded to the pump body 1. It is set as the structure arrange | positioned in the form inserted | pinched between the outer core 38 and the pump main body 1 to be fixed. The rod guide 37 is also provided with a through hole 37a penetrating in the axial direction in the same manner as the anchor portion 36, and the pressure of the fuel chamber on the anchor portion side controls the movement of the anchor portion so that the anchor portion can move freely and smoothly. It is configured not to interfere.

The outer core 38 has a thin cylindrical shape on the side opposite to the part to be welded to the pump body 1 and is fixed by welding in such a manner that a fixed core 39 is inserted on the inner peripheral side thereof. A rod urging spring 40 is arranged on the inner peripheral side of the fixed core 39 with the narrow diameter portion as a guide, the rod 35 comes into contact with the intake valve 30, and the intake valve is pulled away from the intake valve seat portion 31a, that is, the intake valve. Energizing force is applied in the valve opening direction. The suction valve 30 contacts the stopper 32 at the maximum opening. The stopper 32 is formed by stamping a metal plate, and the outer peripheral surface thereof is press-fitted and fixed to the sheet member 31. A part of the outer peripheral surface is a notch, and the notch is configured to always communicate with the recess, and the upstream side of the suction valve communicates with the pressurizing chamber 11. In the present embodiment, the suction valve seat portion 31a and the suction port 31b are formed by the same seat member 31.

The anchor portion biasing spring 41 is disposed so as to apply a biasing force to the anchor portion 36 in the direction of the rod collar portion 35a while inserting one end into a cylindrical central bearing portion 37b provided on the center side of the rod guide 37 and maintaining the same axis. It is said. The movement amount 36e of the anchor portion 36 is set to be larger than the movement amount 30e of the intake valve 30. This is because the intake valve 30 is surely closed. In this embodiment, the rod guide 37 is formed of the same member as the sheet member 31 described above.

Since the rod 35 and the rod guide 37 slide with each other and the rod 35 repeatedly collides with the intake valve 30, a heat-treated martensitic stainless steel is used in consideration of hardness and corrosion resistance. The anchor portion 36 and the fixed core 39 use magnetic stainless steel to form a magnetic circuit, and the rod urging spring 40 and the anchor portion urging spring 41 use austenitic stainless steel in consideration of corrosion resistance.

According to the above configuration, the intake valve portion and the solenoid mechanism portion are configured by organically arranging three springs. The suction valve biasing spring 33 configured as a suction valve portion, the rod biasing spring 40 configured as a solenoid mechanism portion, and the anchor portion biasing spring 41 correspond to this. In this embodiment, any spring uses a coil spring, but any spring can be used as long as it can obtain an urging force.

As shown in FIG. 2, the discharge valve mechanism 8 provided at the outlet of the pressurizing chamber 11 has a discharge valve sheet 8a, a discharge valve 8b that contacts and separates from the discharge valve sheet 8a, and a discharge valve 8b toward the discharge valve sheet 8a. And a discharge valve stopper 8d that determines the stroke (movement distance) of the discharge valve 8b. The discharge valve stopper 8d and the pump body 1 are joined by welding at the contact portion 8e to block the fuel and the outside.

When there is no fuel differential pressure in the pressurizing chamber 11 and the discharge valve chamber 12a, the discharge valve 8b is pressed against the discharge valve seat 8a by the urging force of the discharge valve spring 8c and is in a closed state. Only when the fuel pressure in the pressurizing chamber 11 becomes higher than the fuel pressure in the discharge valve chamber 12a, the discharge valve 8b opens against the discharge valve spring 8c. The high-pressure fuel in the pressurizing chamber 11 is discharged to the common rail 23 through the discharge valve chamber 12a, the fuel discharge passage 12b, and the fuel discharge port 12.

When the discharge valve 8b is opened, it comes into contact with the discharge valve stopper 8d, and the stroke is limited. Accordingly, the stroke of the discharge valve 8b is appropriately determined by the discharge valve stopper 8d. As a result, the stroke is too large, and it is possible to prevent the fuel discharged at high pressure into the discharge valve chamber 12a from flowing back into the pressurization chamber 11 again due to the delay in closing the discharge valve 8b. Can be suppressed. Further, when the discharge valve 8b repeats opening and closing movements, the discharge valve 8b is guided by the outer peripheral surface of the discharge valve stopper 8d so that the discharge valve 8b moves only in the stroke direction. By doing so, the discharge valve mechanism 8 becomes a check valve that restricts the flow direction of fuel. The pressurizing chamber 11 includes a pump body 1 (pump housing), an electromagnetic suction valve mechanism 300, a plunger 2, a cylinder 6, and a discharge valve mechanism 8.

(High pressure fuel pump operation)
When the plunger 2 moves in the direction of the cam 93 due to the rotation of the cam 93 and is in the suction stroke state, the volume of the pressurizing chamber 11 increases and the fuel pressure in the pressurizing chamber 11 decreases. In this process, when the fuel pressure in the pressurizing chamber 11 becomes lower than the pressure in the suction port 31b, the suction valve 30 is opened. As shown in FIG. 4, the fuel flows through the opening 30 e of the intake valve 30 and flows into the pressurizing chamber 11.

After the plunger 2 completes the suction stroke, the plunger 2 starts to move upward and moves to the compression stroke. Here, the electromagnetic coil 43 remains in a non-energized state and no magnetic biasing force acts. The rod biasing spring 40 is set to have a biasing force necessary and sufficient to keep the suction valve 30 open in a non-energized state. The volume of the pressurizing chamber 11 decreases with the compression movement of the plunger 2. In this state, the fuel once sucked into the pressurizing chamber 11 is again sucked through the opening 30 e of the intake valve 30 in the valve open state. Since the pressure is returned to the passage 10d, the pressure in the pressurizing chamber does not increase. This process is called a return process.

In this state, when a control signal from the ECU 27 is applied to the electromagnetic intake valve mechanism 300, a current flows through the electromagnetic coil 43 via the terminal 46. Then, a magnetic attractive force acts between the magnetic core 39 and the anchor, whereby the magnetic urging force overcomes the urging force of the rod urging spring 40 and the rod 35 moves away from the intake valve 30. Therefore, the suction valve 30 is closed by the biasing force by the suction valve biasing spring 33 and the fluid force caused by the fuel flowing into the suction passage 10d. After the valve is closed, the fuel pressure in the pressurizing chamber 11 rises with the upward movement of the plunger 2, and when the pressure exceeds the pressure at the fuel discharge port 12, high-pressure fuel is discharged via the discharge valve mechanism 8 to the common rail 23. Supplied. This stroke is called a discharge stroke.

That is, the ascending stroke between the lower start point and the upper start point of the plunger 2 is composed of a return stroke and a discharge stroke. And the quantity of the high-pressure fuel discharged can be controlled by controlling the energization timing to the electromagnetic coil 43 of the electromagnetic intake valve mechanism 300. If the timing of energizing the electromagnetic coil 43 is advanced, the ratio of the return stroke during the upward stroke is small and the ratio of the discharge stroke is large. That is, the amount of fuel returned to the suction passage 10d is small and the amount of fuel discharged at high pressure is large. On the other hand, if the timing of energization is delayed, the ratio of the return stroke during the upward stroke is large and the ratio of the discharge stroke is small. That is, the amount of fuel returned to the suction passage 10d is large, and the amount of fuel discharged at high pressure is small. The energization timing to the electromagnetic coil 43 is controlled by a command from the ECU 27. By controlling the energization timing to the electromagnetic coil 43 as described above, the amount of fuel discharged at high pressure can be controlled to the amount required by the internal combustion engine.

(Composition of metal damper)
As shown in FIG. 1, a metal damper 9 is installed in the low pressure fuel chamber 10 to reduce the pressure pulsation generated in the high pressure fuel pump from spreading to the suction pipe 28 (fuel pipe). When the fuel that has once flowed into the pressurizing chamber 11 is returned to the suction passage 10d through the intake valve 30 (suction valve body) that is opened again for capacity control, the fuel returned to the suction passage 10d is used as a low-pressure fuel. Pressure pulsation is generated in the chamber 10. However, the metal damper 9 provided in the low-pressure fuel chamber 10 is formed of a metal diaphragm damper in which two corrugated disk-shaped metal plates are bonded together on the outer periphery and an inert gas such as argon is injected therein. The pressure pulsation is absorbed and reduced as the metal damper expands and contracts.

The plunger 2 has a large-diameter portion 2a and a small-diameter portion 2b, and the volume of the sub chamber 7a increases and decreases as the plunger 2 reciprocates. The sub chamber 7a communicates with the low pressure fuel chamber 10 by a fuel passage 10e (see FIG. 3). When the plunger 2 descends, fuel flows from the sub chamber 7a to the low pressure fuel chamber 10, and when it rises, fuel flows from the low pressure fuel chamber 10 to the sub chamber 7a.

This makes it possible to reduce the fuel flow rate into and out of the pump during the pump intake stroke or return stroke, and to reduce the pressure pulsation generated inside the high-pressure fuel pump.

Here, in high-pressure fuel pumps, in recent years, the pressure of discharged fuel has increased (20 MPa or more) and the flow rate has increased. In this case, the inventors have intensively studied that a large force is applied to the suction valve 30 shown in FIGS. 1, 2, and 4 in directions other than the suction valve axial direction (the left-right direction in FIGS. 1, 2, and 4). It became clear. However, in the case of the intake valve structure shown in FIGS. 1, 2, and 4, this movement cannot be restricted when the intake valve 30 is tilted by a force in the radial direction or is shaken in the radial direction. If it does so, the sheet | seat by the suction valve 30 will not be produced, but there exists a problem of causing the flow volume fall or the deterioration of flow controllability. Further, when the suction valve 30 is inclined and comes into contact with the suction valve seat portion 31a, the suction valve seat portion 31a is worn, thereby causing a problem that the seat performance is deteriorated.

Therefore, an embodiment of the present invention will be described with reference to FIG. The valve mechanism of the present embodiment includes an end turn part 33a and a movable part 33b, and is fixed by a spring support part 32a opposite to the end turn part 33a, and an end turn part 33a of the spring member 33. And a valve body (suction valve 30) that is urged by the other side. Further, a convex portion 30 b that is convex toward the spring support portion 32 a and is located on the radially inner side of the spring member 33 is formed in the valve body (suction valve 30). As shown in FIG. 6, in the cross-sectional view passing through the radial center of the spring member 30 and cut in the axial direction of the spring member, the windings on both sides in the radial direction of at least the first turn of the movable portion 33 b adjacent to the end winding portion 33 a. It is comprised so that the front-end | tip part 30c of the convex part 30b may be located in the spring support part 32a side with respect to a line cross section.

The movable portion 33b may be referred to as an effective winding portion, and the movable portion 33b is a portion that actually operates as a spring. Since a gap is formed in the movable portion 33b, when a large force is applied in the radial direction of the valve body (suction valve 30), the valve body itself tilts or swings through the gap of the movable portion. Will do. Therefore, in the present embodiment, as described above, the distal end portion 30c of the convex portion 30b is on the side of the spring support portion 32a with respect to the winding cross section on both sides in the radial direction of at least the first winding of the movable portion 33b (effective winding portion). It is comprised so that it may be located in. In FIG. 6, the end of the winding cross section on both sides in the radial direction of the first winding is indicated by a dotted line. Accordingly, even when a large force is applied in the radial direction of the valve body (suction valve 30), the valve body itself can be prevented from tilting or swinging. Therefore, it is possible to solve the problem that the flow rate is decreased or the flow rate controllability is deteriorated as described above. Moreover, since it can suppress that a valve body (suction valve 30) inclines and contacts the suction valve seat part 31a, the problem that the above-mentioned seat performance deteriorates can be solved.

As shown in FIG. 7, the valve mechanism of this embodiment includes a valve seat (suction valve seat portion 31a) that seals when the valve body (suction valve 30) is seated, and the valve body (suction valve 30). In the state where the seat is seated on the valve seat (suction valve seat portion 31a), in the sectional view cut in the spring member axial direction, the convex portion 30b It is desirable that the tip portion 30c is configured to be located on the spring support portion 32a side. In addition, if the tip 30c of the convex portion 30b is positioned on the spring support portion 32a side with respect to the winding cross section on both sides in the radial direction of at least the second winding of the movable portion 33b, it is possible to further suppress the rampage in the radial direction. It is.

As shown in FIG. 8, the valve mechanism of the present embodiment includes a stopper 32 that restricts movement of the valve body (suction valve 30) in the direction opposite to the valve seat (suction valve seat portion 31a). In a cross-sectional view cut in the axial direction of the spring member in a state where the suction valve 30) is in contact with the stopper 32, the tip 30c of the convex portion 30b is located on the side of the spring support 32a with respect to the half of the total length of the spring member 33. It is desirable to be configured to be located in

FIG. 8 is a cross-sectional view showing the convex portion of the stopper 32 that contacts the valve body (suction valve 30), while FIG. 6 shows the convex shape of the stopper 32 that contacts the valve body (suction valve 30). It is the figure cut by the cross section which cannot see a part. Therefore, FIG. 6 and FIG. 8 show the same state. The stopper 32 is preferably configured to have a cylindrical holding portion 32c that holds the spring member 33 radially inward. The stopper 32 is preferably configured to hold the spring member 33 by the inner peripheral surface of the holding portion 32c and to have a fixing portion 32d that fixes the stopper 32 on the radially outer side of the inner peripheral surface. In this embodiment, since the stopper 32 is formed by stamping, it can be configured at a low cost.

Further, it is desirable that the convex portion 30b of the valve body (suction valve 30) is formed in a cylindrical shape. As shown in FIG. 6, the valve body (intake valve 30) is formed of a cylindrical portion 30d having a low height and a cylindrical convex portion 30b having a height higher than that of the cylindrical portion 30d. The electromagnetic suction valve mechanism 300 of this embodiment is configured separately from the valve mechanism and the valve body (suction valve 30) described above, and biases the valve body (suction valve 30) in the valve opening direction. The rod 35 includes an anchor 36 that drives the rod 35 in the valve closing direction, and a coil 43 that generates an electromagnetic attractive force that drives the anchor 36 in the valve closing direction.

The high-pressure fuel pump of the present embodiment is configured separately from the valve mechanism described above, independent of the valve body, and a rod 35 that biases the valve body in the valve opening direction, and the rod 35 is closed. An anchor 36 that drives in the valve direction, a coil 43 that generates an electromagnetic attraction force that drives the anchor 36 in the valve closing direction, and a pressurization for pressurizing the fuel that is located downstream of the valve body (suction valve 30) The chamber 11 and the plunger 2 that increases and decreases the volume of the pressurizing chamber 11 are provided.

In addition, this invention is not limited to an above-described Example, Various modifications are included.
For example, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations. In addition, it is possible to add, delete, and replace other configurations for a part of the configuration of the embodiment.

DESCRIPTION OF SYMBOLS 1 ... Pump body, 2 ... Plunger, 11 ... Pressurization chamber, 30 ... Suction valve, 30b ... Convex part, 30c ... Tip part, 30d ... Cylindrical part, 31a ... Suction valve seat part, 32 ... Stopper, 32a ... Spring support Part, 32c ... holding part, 33 ... spring member, 33a ... end winding part, 33b ... movable part, 35 ... rod, 36 ...

anchor

36, 43 ... coil

Claims

A spring member having an end winding portion and a movable portion and fixed by a spring support portion on the opposite side of the end winding portion; and a valve body biased by the end portion of the spring member. A convex portion located on the radially inner side of the spring member is formed on the valve body.
In the cross-sectional view passing through the radial center of the spring member and cut in the axial direction of the spring member, the convex portion with respect to the winding cross section on at least the first turn in the radial direction of the movable portion adjacent to the end winding portion. The valve mechanism comprised so that the front-end | tip part may be located in the said spring support part side.
The valve mechanism according to claim 1, wherein
A valve seat that seals by seating the valve body;
In the state where the valve body is seated on the valve seat, in the cross-sectional view cut in the spring member axial direction, the tip of the convex portion is at least the winding cross section on both radial sides of the first turn of the movable portion. A valve mechanism configured to be located on a side of the spring support portion.
The valve mechanism according to claim 1, wherein
A valve seat that seals when the valve body is seated; and
A stopper for restricting movement of the valve body in a direction opposite to the valve seat, and
In a cross-sectional view cut in the spring member axial direction in a state where the valve body is in contact with the stopper, the tip end portion of the convex portion is located on the spring support portion side with respect to a half position of the entire length of the spring member. A valve mechanism configured to:
The valve mechanism according to claim 1, wherein
A valve seat that seals when the valve body is seated; and
A stopper for restricting movement of the valve body in a direction opposite to the valve seat, and
The valve mechanism is configured such that the stopper has a cylindrical holding portion that holds the spring member radially inward.
The valve mechanism according to claim 4,
The stopper is a valve mechanism configured to hold the spring member by an inner peripheral surface of the holding portion and to have a fixing portion that fixes the stopper at a radially outer side than the inner peripheral surface.
The valve mechanism according to claim 4 or 5,
The stopper is a valve mechanism formed by stamping.
The valve mechanism according to claim 1, wherein
The convex portion is a valve mechanism formed in a cylindrical shape.
The valve mechanism according to claim 1, wherein
The said valve body is a valve mechanism formed with the cylindrical part with a low height, and the said cylindrical convex part with a height higher than the said cylindrical part.
A valve mechanism according to any one of claims 1 to 7;
A rod configured separately from the valve body, and biasing the valve body in a valve opening direction;
An anchor for driving the rod in a valve closing direction;
An electromagnetic suction valve mechanism comprising: a coil that generates an electromagnetic attractive force that drives the anchor in the valve closing direction.
A valve mechanism according to any one of claims 1 to 8,
A rod configured separately from the valve body, and biasing the valve body in a valve opening direction;
An anchor for driving the rod in a valve closing direction;
A coil for generating an electromagnetic attractive force for driving the anchor in the valve closing direction;
A pressurizing chamber located downstream of the valve body for pressurizing fuel;
A high-pressure fuel pump comprising: a plunger for increasing or decreasing the volume of the pressurizing chamber.